Spinning machines



' Jan. 21, 1958 l E. M. SAGEHO'MME 1,

SPINNING MACHINES Filed Nov. 16, 1954 IOSheets-Sheet 1 F IG.1.

157 1 135 136 I 5 158 6 I 11 1 3 R 15 i 3 19 1 9. 1.9 26 7 1 3 g I 1192 117 1 21 6 1 I 8 O i 36 0 11 21a 41 8 4 ED 8 I m 1. M g i ./a I Inventor Georges EMSug'h omme Jan. 21, 158' Filed Nov. 16, 1954 G. M. SAGEHOMME 'SPINNING MACHINES 10 Sheets-Sheet. 2

Georges EMSayehomme Aho may Jan. 21, 1958 SAGEHOMME 2,820,336

SPINNING MACHINES Filed Nov. 16, 1954 10 Sheets-Sheet 5 F/as,

Invenfor Gegrgesfil lfiagehomme Afr-army Jan. 21,1958 V 5, M, s HoMM 2,820,336

SPINNING MACHINES Filed Nov. 16, 1954 10 Sheets-Sheet 10 -FlG.15.

Inventor Cr or es EM. Sagehomme Afrorney 2,820,336 SPINNING MACHINES Georges Emile Marie Sagehomme, Heusy-Verviers, Belgium Application November 16, 1954, Serial No. 469,270 Claims priority, application Netherlands May 29, 1951 28 Claims. (Cl. 57-94) This invention is a continuation-in-part of application Serial No. 288,927 filed May 20, 1952 and now abandoned, entitled, Spinning Machines.

The present invention relates to textile spinning machines or frames for conical layer bobbins, comprising rotating spindles and thread guides.

Spinning frames or machines at present known, such as mules or ring frames, have several disadvantages. In mules the spinning of the roving and the winding-on of the thread take place periodically in successive steps, to the detriment of the productive capacity of the machine. In ring frames the drafting of the roving takes place entirely before the twisting and winding-on. All the known ring frames comprise for this purpose arrangements for drafting which have the disadvantage of tending to render the roving fragile. To prevent such fragility while carrying out suitable drafting it is necessary either to support and guide the rovings or slubbings or to give them a temporary or false twist while they travel through the drafting arrangement. Support and guiding can be effected by devices including funnels, eyes or aprons and the like: these devices add to the complication of the frames. False twist is carried out by means of false twist tubes or special drawing rollers but such operations again tend to make the roving undesirably fragile.

Furthermore the system of winding-on by means of a freely rotatable ring fiyer or traveller causes undesirable variation in the tension of the roving.

The present invention has for its object to overcome the disadvantages referred to above.

Accordingly the spinning frame according to the invention comprises rotating spindles, rotating thread guides, a feed roller doubling as a delivery roller, a driving shaft, 21 building motion, the driving shaft controlling the feed roller and the building motion at the same time, winding-on means on which the thread is wound and which are fixed on the spindles, a differential gear, two planet gears mounted within the differential gear, a crown wheel or gear provided within the differential gear, one of the planet gears driving positively the spindles, that is the spindles and said members on which the thread is wound have a speed continually proportional to that of one of the planet gears, the other planet gear positively driving the thread guides, that is the latter have a speed continually proportional to that of the other planet gear, a motor driving the crown gear of the differential gear, a device for automatically controlling said motor speed, two conditioning elements provided in said device, one of those elements being governed by the position of the building motion, a speed regulator operating on said driving shaft and the position of which determines that of the second conditioning element, and a positive variable speed gear provided between said driving shaft and said feed roller, the instantaneous speed of the latter roller being selected so that the winding speed on said members is greater than the delivery speed of said feed roller.

So as to maintain an unvariable winding-on speed, in

spite of the diameter changes of the helices making up the conical layers, it is necessary that the thread guide speed should be constantly variable according to a particular law. Such result is obtained by compelling one of the conditioning elements to follow the building motion position, that is of a device from which the formation of the bobbin depends.

A differential gear allowing two speeds to be added or subtracted, the speed of the thread guides which are driven by one of the planet gears of the differential gear, is proportional to the algebraic sum of the speed of that planet gear forced on the power shaft for the spindles and the speed required of the crown gear of the diiferential gear.

In a preferred embodiment, the building motion includes a slide running between fixed guides and carrying a roller associated with a cam having an alternating rotating motion, a first threaded member mounted within the slide so as to follow the movement of translation thereof, a second threaded member associated with the first threaded member and mounted so as to be unable to rotate, the second threaded member supporting the spindle rails, the first threaded member being rotatably driven by a device actuated by the slide for providing a progressive separation between the thread guide rails and the spindle rails.

In a particular embodiment, to enable control of the machine working as well as to select the starting values for the various speeds so as to adjust them to the imposed conditions for the desired thread manufacture, various regulating devices are integral with pointers arranged so as to move along panels or scales, said pointers being moreover arranged by pairs so as to move along directions at right angle to one another in front of a particular panel on which curves are drawn showing certain features of the resulting thread, in terms of two series of variables indicated respectively along x and y axes according to the movement directions of the corresponding pointers which are conditioned by said variables or by others which are a function of the first ones. A pointer moves according to the speed variations of a motor driving the differential planet gear which is forced on the power shaft for the spindles, the other pointer of the same pair moving jointly with said second conditioning member, thus according to the production speed, straight lines, the angular coefficients of which are proportional with the possible twists, being drawn on the panel relating to said two pointers, the intersection of said pointers representing on said straight lines the particular twist conditions obtained.

In another particular embodiment a pointer moves jointly with the driving member of the variable speed gear provided between the feed roller and said driving shaft, that is in relation with the ratio between the production speed and the feeding speed, the other pointer of the same pair moving jointly with the drivin member of another variable speed gear provided between the building motion and said driving shaft, that is in terms of the frequency of the movement direction reversals of the building motion, curves, each corresponding to the workable drafting and winding-on conditions for a par ticular roving, being drawn on the panel relating to said two pointers, the intersection of the pointers showing on said curves the particular conditions obtained.

Other details and features of the invention will be apparent from the description of the accompanying drawings showing by way of non-limitative example, a particular embodiment of the spinning frame according to the invention.

Figure l is an overall perspective view, with parts broken away, of a section of a spinning frame according to the invention.

Figure 2 is an overall schematic view of the spinning frame shown in Figure 1.

Figure 3 is an elevation view of a thread guide, with parts broken away.

Figure 3A is a detailed sectional side view, on a larger scale, of the upper part of the thread guide of Figure 3.

Figure 3B is a plane view from above corresponding to Figure 3.

Figure 3C is a perspective view of part of said thread guide.

Figure 3D is a detailed side view of the lower part of the thread guide of Figure 3.

Figure 4 is a side view, with parts broken away, of a part of the frame comprising a spindle and a thread guide.

Figure 4A and Figure 4B are two enlarged detail views of elements shown in Figure 4.

Figure 5 is a side view of the building motion.

Figure 6 is a section along line VI-VI of Figure 5.

Figure 7 is a section along line VIIVII of Figure 6.

ldigure 8 is a fragmentary schematic view of Figures 5 an 7.

Figure 9 is similar to Figure 8, but relates to another embodiment.

Figure 10 is a side view of the frame part shown in Figures 1 and 2, relating to the roving supply.

Figure ll is an elevation view, with parts broken away, corresponding to Figure 10.

Figure l2 is a schematic view of part of the control means for the spindle rails.

Figure 13 is a schematic plan view of the control means for the spindles or thread guides.

Figure l4 is a diagram of the electrical connections to 801318 parts of the spinning frame shown in Figures 1 an 2.

Figure l5 is a diagram of an electronic device used for automatic regulation of the speed of the driving motor for the crown gear of said differential gear.

The same reference numerals in the various figures, apply to similar members.

The spinning frame according to the present invention is made up of two wings, each one having two faces, and comprising a series of sections or cells; the two wings are joined to a main (or central) cell, or headstock, which includes the main driving elements of the spinning frame only one wing with several cells, indicated by reference numerals 2 to 7, is shown in Fig. l, the main cell being represented as 1. The other cells such as cells 2 to 7 of the frame are all substantially identical, at least as far as their essential members are concerned. So as not to surcharge the drawings, though, some members have been shown for one or several cells, while other members are shown in other cells.

The cells are formed (Figs. 1 and 4) between crosswise frameworks including a lower crosstie 8 supporting two columns or standards 9 and 10 which are connected at their upper ends by an upper crosstie 11. In the main cell 1, spindle rails and 16 support between them a housing 290 (Figs. 1 and 2) of the main driving elements to be described hereinafter.

Thread guide rails 12 and 13 are mounted on the upper crossties of the various cells. Stanchions 14 (Figs. 1 and 4), sliding on the standards 9 and 10, carry the spindle rails 15 and 16. The thread guides and the spindles go through holes. such as 17 and 18, provided receptively in the thread guide and spindle rails. With the example shown in the drawings, six thread guides, as 19, and six spindles, as 20, are provided for a single cell face. Said thread guide is made up of a hollow conical body 21 of light material (Figs. 3 and 4), coaxial with said spindle and at the upper end of which is attached a steel body 232, the inside surface of which is in the shape of a truncated cone as that of the body 21 and it is an extension of the latter so that the inside surface 22 is in the Shape of a truncated cone for all of its effective length. Thanks to this feature, the roving going through the upper aperture 23 of the thread guide encounters no roughness, nor protruding part.

There is effectively provided, near the aperture 23, a short lengthwise groove 24 (Figs. 3A and 3B), the opening of which is somewhat larger than the diameter of the largest rovings usually utilized. The roving and aperture 23 are of different diameter and the roving rubs against the edge of aperture 23 and is thus caused to roll with a speed dependent on the inverse ratio of the diameters; groove 24 causes the roving to be freed at each revolution from adherence to aperture 23 and, thus, the tendency to twisting is broken. An undue twist of the roving is thus prevented and a shaking is caused, that is a vibrating state of the thread, easing sliding of the fibres on one another, which is favourable to the draft. The inside measurements of the thread guide must be chosen so as to prevent any balloon forming. These measurements are also dependent on those of the bobbin to be formed, which may at no time contact the inside truncated cone.

The housing 21 is cut off on either side, as shown at 26, in its lower part. The purpose of such an arrangement is to make release of the finished bobbin easier. On the lower part 27 of the thread guide are provided two thread guide hooks 28 (Figs. 3 and 3C) which may be made out of porcelain, enamelled metal, hard chrome steel, etc. Some material must of course be chosen which shows a strong wearing resistance. The hooks are formed symmetrically, so that they grip the thread with the thread guide rotating along one direction as well as along the other, depending on whether spinning is done with right or left twisting. The hook 28 include a bushing 29 (Fig. 3C) engaged in a hole with corresponding shape provided adjacent the free edge of the thread guide, that is in part 27. A holding device 30, made up of a steel wire adequately bent, insures interlocking of each thread guide hook 28 and of the thread guide 19.

The thread guide 19 (Figs. 3 and 4) is supported on two ball bearings 128 and 130, the covers 228 and 230 of which are attached to the correpsonding thread guide rail 12.

Above the ball bearing 130 are threaded a spacer 229 then the selected driving member, in this case a chain wheel 25, and finally two tightening nuts 231. A sealing joint 237 (Fig. 4) is provided in a groove of the cover 230. As it will be seen hereinafter, the chain wheel 25 is driven by a chain 182 (Fig. 4B) which is held against the wheel 25 by a metal strip 245 attached to the thread guide rail 12 by parts such as 246, and which is common to all of the wheels 25 in a frame wing face.

Mounting of the spindle 20 (Figure 4) is made in a way similar to that of the thread guide 19, and makes use of the same parts, which of course is interesting as far as interchangeability is concerned. On the spindle 20 is mounted a bobbin tube 114 provided with tenons 247 engaged in slots 248 of the spindle and thus made integral for rotation with said spindle. A tightening device 249 provided with spring projections 251 keeps in position the bobbin tube 114 on the spindle 20.

The thread guide rails 12 and 13 are fixed, but the spindle rails 15 and 16 slide on standards 9 and 10 and go through, with respect to the thread guide rails and along a. direction parallel with the spindle axes, two displacements, one of which changes its direction periodically and is caused by a device called building motion, while the other is a progressive down motion with an unchanging direction. The stanchions 14 of a spindle rail 12 (Figs. 1, 4, 4A and 12) are hooked to chains 31 coupled, in points 234, to a pulling rod 235, after going around return pulleys 236. The pulling rod 235 is mounted so as to keep the chains 31 on the pulleys 236.

There are thus, for each frame wing, two pu ling rods 235, one for each of the spindle rails 15 and 16, said rods being attached to chains 233 hooked to the building motion which will now be described.

The building motion device is driven by a cam with an alternating rotating motion. Said cam, indicated as '32, is shown in Figures 1, 2, 5 and 6. The cam 32 cooperates with a roller 33 supported by a slide 34 moveable between guides 35 and 36 attached to a channel iron 37, set between the crossties 8 and H which are in the left hand part of cell 1 (Figure l). The guides 35 have an inclined surface 291 (Fig. 7) enabling a possible tak- 'ing up of play.

The cam 32 is fixed on a shaft 38 driven by a shaft 39 through a mechanism 46 (Figures 1 and 2), for periodically reversing the rotating direction of the shaft The shaft 39 is driven through a positive variable s eed gear 41 by a motor 63 which is preferably a three phase motor with a shunt type slip ring, such as the repulsion-induction motors with speed regulation through brush displacement.

The mechanism 4t includes, in a way known per se, a sliding gear 42, the movement of which, parallel to shaft 38, causes driving of said shaft either in the rotation direction of shaft 39, or in the opposite rotation direction. A selector fork d3 engages a corresponding groove of the sliding gear 42 and is integral with one of the arms 4 of a lever swivelling in 45' and the other arm 46 of which is hinged on a rod 47, sliding in bearings 48 carried by the channel iron 37. Details of the arrangement of the rod 4-7 are shown in Figures 5, 7 and 8. The rod 47 carries four steps, preferably with adjustable positions and indicated respectively in 49, 5t), 51 and 52. The slide 3 5 carries a plate 53 and a part 54 slipped on the rod 47. Compression springs 55 and 56 are threaded on the rod 47, on the one hand between the stop 51 and the part 54, and on the other hand between the part 5d and the stop 52.

In Figure 5 is shown the slide 34 in its lowest position. Now, in the plate 53 as well as on the rod 47 are provided notches indicated at 57, 58, 59 and so. A bolt 61, slidable in a sleeve 62 carried by the guide 36, is made up of a rod the ends of which are shaped so as to be able to engage the notches 57 to 6d. The bolt length equals the distance between the notch bearing faces of the rod 47 and the plate 53, increased by the depth of one of the notches. The bolt 61 thus cannot move vertically but can slide horizontally. in the position shown in Figure 5, the part 54 occupies, in relation to the rod 47, such a position that the springs 55 and 56 are loosened. Moreover, the bolt 61 is at the level of the notches 58 and 6h. The selector fork 43 occupies its farthest right hand position so that the rotation direction of the cam 32 is presently reversed. The slide will thus start going upwards. Thereby the bolt 61 is pushed back in the notch 5'8 and it thus locks the rod 47 in its lower position. In Figure 8, the arrangement is shown when the slide has already gone through part of its upwards movement. Since the rod 47 is locked by the bolt 61, the part 54 driven by the slide 34 compresses the spring 56. When the slide will come to the end of its upwards movement, the notch 59 will be in register with the bolt 61 and said bolt will be able to move to the left, so as to free the rod 4 7 which will move suddenly upwards, the spring 56 being set, the stops 49 and 52 being then engaged between the bearings l3. The arms 46 and 4d swivel drawing the selector fork 43 to the left, causing a new reversal of the rotation direction of the cam 32, hence of the slide 34.

It is also possible to control the selector forl; 43 by other means shown in Figure 9. The arm 4 swivels in 45-and its end 259 is articulated on the middle part of a rod 266 joining the cores 261 and .262 of two electromagnets 263 and 264. The supply circuits for the latter have a common bus 265 and are connected to a power supply 266 which is connected to a single two way (s. p. d. t.) switch.

The slide 34 carries two micrometric screws 268 and 269 controlling, each in turn, the switch 267. In Figure 9 is'shown the slide 34 as it nears the end of its-upwards travel. The supply circuit to the electromagnet 263 is closed by the switch 267 so that the core 261 is attracted and maintains the arm 44, and thus the selector fork 43, pushed to the right. The slide having completed its upwards travel, the screw 269 pushes the switch 267 in the opposite direction, thus cutting off the circuit to the electromagnet 263 and closing that of the electromagnet 264. The core 262 is attracted, the rod 260 moves to the right and the arm 44 to the left, which produces a reversal in the rotation direction of the cam 32, so that the slide 3 can start its downwards travel. As said travel is being completed, the screw 268 shifts the switch 267 and the whole process starts over again.

It is known that to obtain the formation of succeeding conical layers, it is necessary to cause a downwards motion of the spindle with respect to the thread guide, after each layer formation. It is thus a progressive separation of the thread guide rails and the spindle rails and no more as in the case of the building motion, an alternating relative movement but a relative movement along a steady direction. Now it is substantially impossible to produce instantly such a movement between two thread layers. The relative movement of the spindles with respect to the thread guides must thus take place during a layer formation, producing of course variation of the pitch. To prevent unevenness in the layer, there is provided a changing of the pitch from one end to the other of a building motion travel. There is provided for this purpose two threaded members in the slide 34 (Figs. 6 and 7), one of which is a screw 6 rotatable with respect to the slide, the other is a nut 65 slidable with respect to the slide but the rotating motion of which is prevented by means of the outside shape given it. The chains 233 which are attached to the pulling rods 235 are fixed to the nut 65.

The screw 64 may be driven by means of a vertical shaft 66; said shaft is fluted and allows the lengthwise movement of the screw with its supporting slide. Two wedges 67, set in the screw head, are indeed engaged in the wedge grooves 68 of the shaft 66.

There are provided two running ways 69, 7t}; 71, 72 inclined with respect to the movement direction of the slide 34 and symmetrical about said direction (Figs. 5 and 6); both running ways are thus arranged in the form of a V, each one is made up of two parallel bars, indicated respectively in 69 and 7d, and in 71 and 72. These bars are supported respectively on shafts 73 and 74 housed in a tail 75 of the slide 34. The bars 69 to 72 may thus swivel on their upper ends. The lower ends of these bars are joined by two link-pins, such as 76, said link-pins making up a nut 77, while resilient clamping rings 78 insure the desired position of the various bars. A screw 79 goes through both nuts 77, said screw being part right handed thread and part left handed thread (Figures 5 and 6). In its middle part the screw 79 goes through a studhole 86 provided in part 81 mounted on a flange 82 of the slide 34. Rings 83 fixed on the screw 79 on either side of part Sll prevent any lengthwise movement of the screw 79. By rotating the screw 79, the ends of the bars 69 to '72, depending on the selected rotation direction, are caused to come together or away from one another. The slope of the two running ways is thus correspondingly varied.

Extensions 84 and 85 (Fig. 5) are attached to the U iron 37. They carry rods 86 and 87 on which are mounted two carriages 88 and 89 supporting shafts 90 and 91 on which are set two pairs of grooved pulleys 92 and 93 and, for each pulley pair, two rollers 94 and 95. A cable 96 is attached for instance in point 97 of the extension 84. Said cable goes then around one of the pulleys 93, after which it goes around a pulley 92, then around a reversing pulley 98 mounted on a support 99 attached to extension 85. The cable 96 finally goes around a drum 100 idly mounted on a horizontal shaft 101.

The vertical shaft 66 is driven through'bevel gears 102 7 101 (Fig. 6). The drum 100 is fixed to one of the discs 103 of the claw coupling 104 driving in one direction only. The second .disc 105 of the coupling 104 is fixed to a sliding collar 106. Said sliding collar is mounted on the shaft 101 so as to rotate the latter but to be slidable thereon.

When, under action of the cam 32, the slide 34 goes up causing the up motion of the spindle rails 15 and 16 and of the spindles they carry, the running ways formed by bars 69 to 72 follow the up motion. There results the spacing from one another of the rollers 9 and 95 which run on the bars 69 to 72, and the same goes for pulleys 92 by the horizontal shaft and 93. Thereby, in spite of the opposing action of a counterweight 107 terminating the cable 96, the latter comes unwound on the drum 100 and drives it, which drum through the coupling acting precisely in said rotation direction, drives the horizontal shaft 101 and through the gears 102 the vertical shaft 66. The screw 64 rotates causing a relative down motion of the nut 65 with respect to the slide 34.

In view of the arrangement shown for the two running ways, the change of pitch is made during the up motion of the spindles. However, the runnings ways might be arranged in the opposite way, that is with the apex of the V downwards, the change of pitch then being made during the down motion of the spindles.

In the present case, during the down motion of the slide 34, the rollers 94 and 95 come nearer under the action of the counterweight 107, driving the drum 100 in the direction opposite to the preceding one, the coupling 104 being at the time inoperative.

It is to be noticed that it is possible to wind the cable 96 several times around pulleys 92 and 93 affording a first possible means for controlling within large limits the progressive down motion of the rails and 16. A finer control may be obtained by rotating the screw 79, that is by getting the lower ends of the bars 69 to '72 to come more or less closer, as previously indicated.

When the winding of the bobbins is finished, all of the members of the frame are stopped and it is necessary to withdraw the bobbins, that is to release them from the thread guides. This is achieved by causing further down motion of the rails 15 and 16. For this purpose there is provided a groove 10% in the sliding collar 106 (Figure 6). A fork 109 (Figures 2, 5 and 6), swiveling in 110, is engaged in the groove 100. At its other end it is fixed to the rod 111 carried on the core 112 of an electromagnet 113 (Figure 2).

There results from the foregoing that during the formation of the bobbins, the nut 65 goes progressively down with respect to the slide 34. Said nut when the bobbins are ready to be withdrawn is in a relative middle position with respect to the slide 34.

There is shown in Figure 2 a bobbin in process of formation, in cross section for its right-hand part, which shows the succeeding conical layers formed on the bobbin tube 114 set on a spindle 20. Not only is it thus necessary to lower the spindle rails 15 and 16 to release the tubes 114 from the thread guides 19, but also to release these tubes 114 from the corresponding spindles 20. For this purpose there is provided a bar framework 115 for each cell. Two bar frameworks 115 are shown in Figure l, in the cells 4 and 5. Each bar framework 115 comprises a horizontal rod 116 mounted on arms 117 fixed on a rod 110 going through the columns 9. The rod 116 is long enough to allow the bar framework to enclose the spindles of a cell. A similar arrangement is provided on the other face of the spinning frame, the corresponding horizontal rod going through the standards 10.

During building up of the bobbins, the bar frameworks are displaced towards the middle lengthwise plane of the spinning frame. When the bobbins are completed the bar frameworks are brought closer so as to engage the rods 116 bewteen the spindle rails 15 and 16, and the bobbins. In Figure 2 is shown a rod 116 in the position it would occupy with respect to the bobbin if it were in its completion position.

The rod 118 is controlled in the cell 1 by means of a working lever 119 which may have two positions, one of which corresponds to the displacement of the bar frameworks and the other to the engagement of the bar frameworks between the spindle rails and the completed bobbins (Figure 1).

It has been shown it is possible to control the movement of the sliding collar 106 by means of the electromagnet 113. There is provided besides a loading spring 123 (Fig. 2) continuously trying to bring the disc towards the disc 103, that is to make the coupling 104 operative. A small electric motor 122 (Figs. 2 and 6) is able through the bevel gears 120 and 121 to drive the horizontal shaft 101. Thus, if the switch 126 being closed, the switch 124 (Figure 14) is closed, and thus the supply circuit to the electromagnet 13, the sliding gear 106 is cause to move to the right against the working of the loading spring 123. The drum 100 is disconnected and, as the core 112 of the electromagnet 113 gets to the end of its travel, it closes a switch inserted in the supply circuit of the motor 122. Said motor thus starts rotating in the suitable direction for the further lowering of the spindle rails, if the switch 126 is in the position corresponding to the rotation direction of the motor 122 which lowers the spindle rails and which is the left hand position in Figure 14. When the spindle rails come to their lowest position they open an end of play switch 127, which results in breaking the supply circuits to the electromagnet 113. The loading spring 123 then pushes the disc 105 back towards the disc 103 and the core 112 of the electromagnet 113 towards the right (Figure 2); the circuit to the motor 122 is then cut off due to the opening of switch 125.

If, after putting bobbin tubes 114 back on the spindles 20, it is desired to raise the spindle rails 15 and 16 to start a new spinning operation, it is necessary to raise said spindle rails up to the highest position they must have with respect to the thread guide rails. To this end the position of the switch 126 is first changed over so as to reverse the rotation direction of the motor 122. The switch 124 is then closed which results in disjoining the discs 103 and 105 under the action of the movement of the sliding collar 106. Besides, as above, the core 112 reaching the end of its travel closes the switch 125 and the motor 122 starts its rotation so as to raise the spindle rails. When the latter ones come to the end of their upwards motion they open an end of play switch 129. This results in breaking the supply circuit to the electromagnet 113 and in opening the switch 125, thus to stop motor 122.

There are shown in Figures 10 and 11, as well as in Figure 1 some details of the roving supply to the spinning frame. It is achieved by means of devices of known type for supplying roving, such as bobbins, the shafts of which are engaged in either one of the grooves 131 provided in plates 132. Use is made of the central groove if a single roving bobbin is provided for both faces of the spinning frame, or of the two outside grooves if there is provided a roving bobbin for each face of the spinning frame. in the first case the odd roving coils feed one of the frame faces, the even coils the other frame face. The plates or flanges 132 are set on three tubes 133 and attached to a holding down rod The tubes 133 are threaded in a series of supporting plates 135, each one being carried on the upper part of a vertical upright 136 mounted in the crosstie 11 of each crosswise framework. Six parallel rollers 137 (Figs. 10 and 11) are arranged between the supporting plates 135. They are covered with a rubber layer 292 (Figs. 10 and 11) and are used for feeding the roving coils carried by the roving bobbins. Said rollers are integral with chain wheels 139 coupled by a chain which ensures the rotation of the six rollers along the desired directions. The chain itself is driven by a grooved pulley with variable section another pulley 142 140 around which is trained'a belt 141 going also around mounted on one of thetwoshafts 143 comprising the feed cylinders. 'A'pulley 144, with ad- 'justable position, enables to control the speed of the rollers 137 with respect to the speed of the feed rollers 143, by varying the tension of the belt 141 which penetrates more or less deeply in the groove of the pulley 140, the flanges of which spread correspondingly against a loading spring 27f).

The feed rollers 143 (Figs. and 11) are supported in bearings provided in parts 145 which are also carried on the centre uprights 13d of the crossties 11. Between the parts 145 are mounted shafts 146, arranged in prolongation of one another and carrying pairs of swiveling arms, such as 147, one of which is assumed to be rotated in the plane of Figure 11, to enable to see more clearly the members it carries. As a matter of fact pressure rollers, such as 148, are mounted on the arms 147 and rest on the feed rollers 143. Swiveling strips 149 are also arranged on the arms 147 and enable to press a felt 150 which affords cleaning of the pressure rollers. The

joint of the strips 149 carries a small part 250 opened in the form of an eyelet and used for the passage of the roving which, coming from the roving bobbins, will pass on the feed roller 143.

There is provided, for regulating the pressure of the rollers 148 on the feed cylinders 143, links 151 articulated on the arms 147 and connected to a spring 152 the second end of which is attached to a lever 153 forced on a shaft 154 carried on the crosstie 11. The shaft 154- is thus common to all of the levers 153 and by rotating said shaft the pressure of all of the rollers 148 can thus be regulated. In Figure 1 there is shown that the shaft 154 is integral with a working lever 155 moveable in front of a toothed sector or quadrant 156 so as to occupy the various desired positions.

The roving leaves the feed roller in a non-attenuated state and therefore in a less fragile condition than in an ordinary frame, and is immediately subjected to twisting. As drafting cannot take place in a roving which is fully twisted, an adjustable twist reducing device or twist barring, comprised of a rod 157 over which goes the roving, is provided between each feed roll-er 143 and the thread guides 19. There has indeed been noticed that a greater or lesser pressure on the roving in course of twisting will reduce more or less the transmission of this twist along the roving beyond the point where the pressure is applied and can even prevent any twist from being transmitted at all. In the present case the twist barring 157 (Figs. 2, 10, and 11) enables to reduce the twist transmission towards the feed roller 143. The rod 157 is threaded in the drilled ends of the supporting rods 158 slidable in brackets 159 carried on crossties 11. The second ends of the supporting rods 158 rest on the ends of 'the levers 161D forced on two shafts 161, also carried on the crossties 11. The two shafts 161, running parallel to one another along the whole of the spinning frame, can be driven at the same time or one at a time by one or two working arms. In the first case use can possibly be made of a screw device with right and left hand thread similar to that which enables to regulate the spreading of the building motion running ways, said screw 228 being controlled by means of a handwheel 227 (Figures 1 and 2).

In Figure 10 have been shown, to the left and to the right, the rods 158 in their two farthest positions.

Between the vertical uprights 136 are mounted T irons 162 shown in Figs. 1 and 10 and which support sloping sheets 163 and 164, in which holes 165 are provided with a funnel, said holes being prolongated by parallel pipes 166 terminating in collecting tubes 167 and 168, one for each face of the frame. Said tubes open, at the end of the machine, in a tank. A Vacuum iscreated in the tank and in the collecting tubes 167 and 168, for in- "stance by means of a blower or fan. The holes165 are erati'on a roving happens to break, I responding hole 165, it is sucked into the pipe 166 and provided in such a way that if during the spinning opit falls in the coreithcr'of the collecting tubes 167 and 168, so as to be subsequently collected in the tank to return it to the spinning preparing machines. It is 'to be noted that, in opposition to what happens in the known spinning frames, when breaking occurs the thread is not tied again. On the one hand, in the spinning frame according to the invention, the number of breaks is specially reduced. On the other hand, if breaking occurs anyway, which can always happen due to faulty preparation of the roving, the corresponding bobbin remains in the condition it was in when the break occurred and it is not completed. The case however is extremely scarce for, in the described spinning frame, the suppression of the drawing rollers, of the false twist tubes, of the tensions due to the'balloon and to the freely rotatable ring flyer or traveller, disposes practically of all breaking causes.

There has been stated previously that the building motion is driven by an electric motor 63 through a variable speed gear 41. The motor 63 also drives the feed rollers 143 through a positive variable speed gear 169 (Fig. 2). Both variable speed gears 41 and 169 may be of the chain type known as P. I. V.

The spinning frame is provided with a differential gear 170 (Fig. 2), a planet gear 171 of which is forced on a shaft 172 driven by the main motor 174 which is pref erably a three-phase motor with a shunt type collector, such as the repulsion-induction type motors with speed regulation by brush displacement. On the fluted shaft 172 is mounted a rotation direction reversing device 175 comprised of a bevel gear 176 mounted on the shaft 172 so as to be rotated by said shaft but to be slidable thereon. A fixed gear 177 compels another bevel gear 178 idly mounted on the shaft 172 to rotate in the opposite direction to that of the gear 176. The gear 178 is integral with a chain wheel 179 driving the endless chain 18% which rotates the spindles 20.

The differential gear 170 comprises a second planet gear 173 idly mounted on the shaft 172 and integral with the chain wheel 181 driving the endless chain 182 which rotates the chain wheels 25 of the thread guides 19.

The chains 180 and 182 are arranged in the same way. In Figure 13 there is shown the arrangement for the chain 132.

One of the sides, thread guides in one side 239' drives the 233, of the chain 182 drives the of the frame faces, while the other thread guides in the other face. There are actually two chains 182 which relates to the two wings of the frame and which are both driven by the chain wheel 181 and go around the guiding wheels 240. Moreover, each. chain 182 is kept in place by a chainguard 241. Stretchers or take up members 2523, 253, 254 and 2.55 are provided between the guiding wheels 240 and the chain wheels 25; they are mounted on arms 24-2 which are biased by springs 243. In Figure 13, the chains are assumed to be motionless, the four take up members then being symmetrical. If the Wheel 181 rotates along the direction of the arrow 244, the take up members 253 and 255 move away from the lengthwise axis of the frame, so as to take up the slack in the driven sides 239.

At the end of the frame, each chain 182 goes around two wheels 256 and 257, the axes of which can be pushed towards or away from one another by rotating a screw 258 with rightand left-handed thread.

There results from the foregoing that the spindles 20, that is the tubes 114 on which the thread is wound, as well as the thread guides, have an instantaneous speed constantly proportional, respectively, to that of the planet gears 171 and 1'73; in other words said various members are positively driven.

The crown wheel 183 of the differential gear 170 'is driven through a worm-screw 184, by'an electric motor =nating current (A. C.) net a secondary winding 272 of which supplies two thyratrons for 'direct current (D.

273 and 274, the grids of which are connected through phase shifters 275 and 276 to taps on the secondary winding 272, the center tap of which is connected to the armature 277 of the motor 185. Each phase shifter is made up of an inductance and two potentiometers 1 87- and 188.; Both phase shifters are mechanically locked together, but the potentiometers 1t and 138 can be varied separately.

The transformer 271 is provided with another secondary winding 2'79 supplying two rectifiers 281] and 231 which are usedfor the direct current (1). C.) supply to the: shunt field 2320f the motor 185.

By varying the values of the potentiometers 137 and 188, phase shift is applied to the grids of the thyratrons 2'73 and 2'74 and it is possible to vary the voltage across the-armature of the motor 135 within large limits, which gives a wide range of speed control. The potentiometers 187 and 188 are conditioning elements, one of which is controlled by the position of the "building motion and the other by a member 189 enabling to regulate the speed of the motor 63 which drives the driving shaft 190 operating the feed rollers 143 and the building motion. it is to be noted that the drive of the feed rollers 143 and that of the building motion are also positive drives just like the one of the spindles 2t) and of the thread guides 19.

The instantaneous speed of the shaft 19% being chosen, the delivery speed of the feed rollers 143 is selected so that it is slower than the winding speed on the tubes 114, so that drafting of the roving occurs between the feed rollers 143 and the thread guides-spindles units. This explains why the drafting rollers can thus be dispensed with.

Conditioning of the potentiometer 137 by the position of the building motion is effected by driving the slider of said potentiometer through a with a rack 1572 cut in a rod 113 carrying a roller 1% cooperating with a cam 195 mounted on the driving shaft 38 of the building motion.

There is provided according to this invention, means for determining and regulating at working conditions of the machine. For this purpose the spinning frame comprises two panels 1% and 197 (Figures 1 and 2), made up of transparent plates in which lines are carved re roducing various curves mentioned hereinafter. Behind the two panels move pointers indicated in 1%, 19%, and 291. The pointers 198 and 199 are associated with the panel or scale 1%. To pointer 198 is attached a band 2112 going around a pulley 203 which is joined through, for example, a flexible shaft 2-124 to a device 295 enabling to control the speed notor 1'74, for example by displacement of the a simple or. the llatter bushes. To the pointer 191i is attached a band 206 going around a pulley 297 which is joined, for example through a flexible shaft 21323, to the slider of the potentiometer 185. "I he band 2% is also trained around a pulley 2&9 which is joined through a flexible shaft 210 to the device 189 enabling to vary the speed of the motor 63.

The means for providing the various desired adjustnents will, for ease of understanding, be described with the help of a numerical example.

Let it be assumed that a thread of 12 count and having l-O turns of twist per meter is to be produced from a roving of 9.6 count.

' "If, depending on the quality of the roving it is desired gear wheel 191 meshing I all times the to spin at a rate of 10 meters per minute the spindles must be given a speed of rotation of 1OX450=4,500 R. P. M. By turning the pulley 203 which may be provided for this purpose with a driving knob, the speed of the motor 174 can be varied, and thus the speed of the spindles, and the pointer 1955 is moved, pointer which is movable with respect to a scale graduated in spindle R. P. M.

The diameter of thefeed roller 14-3 will be assumed be 31.85 mm., when it will have a circumference of mm; for a 1/1 ratio in the variable speed gear 169, that is to say without draft, and to feed the roving at 10 meters per minute, the feed roller must thus rotate at 10,000/l00=1()0 R. P. M. If the gear ratio between the shaft and the variable speed gear 169 is for example 19/1 the drive shaft 1% must rotate at 10 100= 1000 R. l. M.

By turning either the pulley. M7 or regulation of the motor 63 is obtained the pulley 209, through the de- 7 vice 181 and at the same time the resistance value of the potentiometer 188 is regulated relative to the speed of the motor 63, thus of the shaft 1% and of the production speed. The pointer 1% follows the movement of the band 266 and is movable with respect to a scale marked in speeds of production of meters per minute.

The twist is given in turns per meter per the quotient of the spindle R. P. M. and the production speed in meters per minute. it is thus possible to draw on the panel 1% a series of straight lines, such as 226, which pass by the point with coordinates 0,0 and the angular coefficient of which will be proportional to the twist. it is thus possible to graduate said various lines in twists. When, during the working, control of the spindle or production speed is effected, at the point of intersection of the pointers 198 and 19? may be automatically read the amount of twist. Adjustments may similarly be made by having the intersection of the pointers 198 and 1% follow the desired twist line.

The arrangement of the panel 197 is similar to that of the panel 196. The pointer 200 follows the movements of the band 211 which is trained around the pulley 212 joined through a flexible shaft 213, to the driving mem her 214 controlling the variable speed gear 169, and enables thus to determine the feeding speed with respect to the speed of the production shaft 1%.

The pointer 201 follows the movements of a band 215' which is trained around a pulley 216 of a type somewhat different from that of the pulleys 293, 207, 209 and 212. Said pulley 216 includes an external knob 217 cooperating through a flexible shaft 218 with a driving member 219 for the variable speed gear 41 which, as stated above, is provided for varying the speed of the shaft 39 relative to the thread diameter, that is the frequency of the motion direction reversals of the building motion" and thus of the spindle rails 15 and 16. There results then a change in the winding rate of the thread on the bobbins and in the amount of thread wound on each complete layer (upwards and downwards), that is of the needlefull.

The pulley 216 also comprises an inside knob 220 which is normally integral with the outside knob 217 and which is joined through a flexible shaft 221 to a fluted shaft 222 (Figures 2 and 5), on which a bevel gear 223 is mounted so as to follow the rotation of the shaft 222 but to be able to move lengthwise with respect to said shaft. The gear 223 meshes with another bevel gear 224 fixed on the screw 79, mentioned previously.

By turning the knob 220 the distance between the running ways is adjusted, and thus the rate of the progressive down motion of the spindles 15 and 16. Said adjustment must be done depending on the thread diameter. Working of the pulley 216 thus is used for the various adjustments of the relative movement, alternating as well as unidirectional, between the spindle rails 15 and 16 and the thread guide rails 12 and 13, according to the thread diameter.

When the knobs 217 and 220 are coupled to one another, which isthe normal arrangement, turning ofthe pulley 216 varies the slope or tilt of the running ways depending on the position of the variable speed gear 41. However, depending on the thread nature, it may happen to be necessary to alter the adjustment of the slope of the running ways. In such a case, the knobs 217 and 220 are uncoupledand the in side knob 217 only is turned to adjust the rate of the progressive spreading of the spindle and thread guide rails for a particular frequency of the movement direction reversals of the building motion.

It has been indicated that the speed control of the motor 63 by means of either of the pulleys 207 and 209 is automatically followed by an adjustment of the potentiometer 188. The electronic device 186 then influences the basic speed of the motor 185 driving the crown gear 183 of the diderential gear 170. Said basic speed is the speed which obtains the desired speed of windingon on the greatest diameter of the thread Winding cone on the bobbins; it is, in the example given, 10 meters per minute. Let it be assumed that the cone has a base diameter of 100 mm. and a diameter of 25 mm. at the top.

To wind on the thread at 10 meters per minute on the 100 mm. diameter, l0,000/3.14 l=31.85 R. P. M. speed difference must exist between a thread guide 19 and the corresponding spindle 20, thus the thread guide speed must be 4,531.85 R. P. M. with the given speed of 4,500 R. P. M. for the spindle. The speed of the thread guide is obtained by means of the differential gear 170 and results of the sum of the speed of the planet gear 171 and that of the crown gear 183. The planet gear 171 is fixed to the shaft 172 which drives the spindles and rotates thus at a speed proportional to the spindle speed, for example 1,500 R. P. M., if the ratio between the speeds of the shaft 172 and the spindles 20 is l/ 3. The additional speed, or winding-on speed, is introduced to the differential gear 170 through the crown gear 133. If the ratio between the gears of the differential gear is 1/1 and the ratio between the second planet gear 173 and the thread guides 19 is Vs the speed of rotation of the crown gear will be 31.85/3=l0.61 R. P. M. If the ratio between the speed of the crown gear 183 and that of the motor 185 is /1 the speed of the motor 185 will be l0.61 10:106.1 R. P. M. which is the basic speed of said motor.

The potentiometer 188 is adjusted to give the motor 185 this speed of 106.1 R. P. M., for the corresponding speed of rotation of 1,000 R. P. M. given to the motor 63, since at this moment the slider of the potentiometer 187 is at the end of its travel corresponding to the large diameter of the winding-on cone, thus to the highest position of the spindle rails and 16 for the thread layer in the course of winding-on.

To maintain a constant winding-on speed in spite of the diameter changes of the turns making up the conical layers, it is necessary that the thread guide speed varies con tinually according to a particular variation law.

To wind the thread at the same winding-on speed of 10 meters per minute on the diameter of 25 mm., the difference between the speeds of the thread guide 19 and the corresponding spindle 20 must be 10,000/3.14 =l27.4 R. P. M., or 4,627.4 R. P. M. of the thread guide and 4,500 R. P. M. of the spindle.

At this moment the speed of the motor 185 which drives the difierential gear will be 127.4 10/3=424.3 R. P. M. The variation of speed of the motor 135 from 106.1 to 424.3 R. P. M. is obtained by means of the potentiometer 187, the slider of which is coupled to the gear 191 the motion of which is related to that of the building motion, the potentiometer 188 remaining at its predetermined setting above described.

The resistance of the potentiometer 187 varies continually jointly with the position of the building motion, that is with a device on which depends the bobbin forma- 14 tion, and thus in terms of the instantaneous diameter of the turn being formed.

In the foregoing calculations the speed of the production shaft 190 is determined on the basis of a delivery speed equal to the winding-on speed (i. e. with a ratio l/l in the variablespeed gear169). But in the present case it is proposed to obtain the thread of 12 count from a roving of 9.6 count, i. e. 25% of draft. As above stated the speed of winding-on has been adjusted to 10 meters per minute by regulation of the speed of the shaft 190. To effect drafting it is merely necessary to run the feed roller 143 at a slower speed by reducing the ratio of the variable speed gear 169 which is obtained by adjustment of the pulley 212 driving the member 214 until the roller 143 turns at R. P. M. instead of R. P. M. for the original setting previously mentioned, the setting of the speed of the shaft 1% remaining of course constant. The pulley 212 drives the pointer 200 which is movable with respect to a scale marked in percentages of draft.

The rod 200 moving according to the draft and the rod 201 moving according to the thread diameter, it is possible for the determination of the pitch to draw a series of curves, such as 225, each one corresponding to the drafting and winding-on conditions for a particular roving.

When, during the working, adjustment of the drafting or the conditions of winding-on is eliected, it is possible to automatically read, at the point of junction of the pointers 200 and 201, the count obtained. it is similarly possible to realise adjustments by having the intersection of the pointers 200 and 201 follow the curve 22-5 relating to the roving being spinned.

All of the adjustments of the spinning frame can thus be effected by turning the pulleys 203, 267, 2125 and 21d according to the particulars given by the two pa els 1% and 107.

The numeric example chosen relates to the case the thread guides rotate faster than the spin cs, but th line of argument pursued can also be applied to the case where the complementary speed due to the motor is subtracted from the spindle speed to give the thread guides their speed.

it must be understood that the difference w. exist between the spindle speed and the is a relative speed difference, the thread gui be maintained unvariable, the complement. i w to the motor 185 then being subtracted from or added to the spindle speed.

There results from the foregoing that in the spinning frame according to the invention, the spindl guides and the feed roller, said roller dou n as a delivery roller, are positively driven, the drafting being effected between the feed roller and the spindle-tread guide units, which explains why the drafting rollers can thus be dispensed with. The thread leaves the feed roller and is subjected to twisting as a roving in a non attenuated state, and without having to be subjected to the harmful effect of the false twist tubes or other members, thereby in a less fragile condition than in an ordinary frame; moreover it is already drafted for a part of the final drafting.

The winding-on speed is automatica ly 1.

a constant value, in spite of the varia one in the diameter of the helices undergoing the winding-on operation; moreover, as the thread is being guided in. the conical thread guide, it does not stand out any freely rotatable traveller and ring liyer do no ymorc; all of the variations in the thread tension are thereby avoided and the breaks are nearly completely done away with. The production capacity and the eiiicienc are in creased.

All the settings and adjustments of the spinning frame are effected in the central or main part of latter; con trol of the Working is readily obtained and it is thus possible to cut down considerably the number'of people which were previously in charge of the control and supervision of the spinning frames.

I claim:

l. Spinning frame comprising rotating spindles, rotatmg thread guides, a feed roller doubling as a delivery roller, a driving shaft, a building motion, the driving shaft driving at the same time both the feed roller and the building motion, members on which the thread is wound and which are fixed on the spindles, a differential gear, two planet gears mounted within the differential gear, a crown gear being provided within the diiferential gear, one of the planet gears driving positively the spindles, that is the spindles and said members on which the thread is wound, have a speed always proportional to that of one of the planet gears, the other planet gear driving positively the thread guides, that is said guides have a speed always proportional to that of the second planet gear, a motor driving the crown gear of the differential gear, a device for automatic speed control of said motor, two conditioning elements provided in said device, one of said elements being tied to the position of the building motion, a speed control device controlling said driving shaft and the position of which determines that of the second conditioning element, and a variable speed gear arranged between said driving shaft and the feed roller, the instantaneous speed of the latter roller being selected in such a way that the winding speed on said members is greater than the delivery speed of said feed roller.

2. Spinning frame as claimed in claim 1, in which at the end of the thread guide opposite to that carrying the thread guide hook, there is provided a short lengthwise groove the opening of which is somewhat larger than the diameter of the larger roving generally used.

3. Spinning frame as claimed in claim 1, in which there are provided pointers, panels along which said pointers can be moved, curves drawn on said panels, means for coupling said pointers by pairs for moving along directions at right angle to one another along a particular panel, the curves on said panel indicating certain features of the produced thread, in terms of two series of variables marked respectively along x and y axes according to the movement directions of the corresponding pointers conditioned by said variables or by others which are functions of the first ones. 1

Spinning frame as claimed in claim 3, in which there is provided motor driving that planet gear of the differential gear which is forced on the power shaft for the spindles, one of said pointers moving in relation to the speed variations of said motor, the other pointer of the same pair moving jointly with said second conditioning element, thus in terms of the production speed, straight lines the angular coefiicients of which are proportional to the workable twists, being drawn on the panel relating to said two pointers, the intersection of said pointers represcnting on said straight lines the particular twist obtained.

Spinning frame as claimed in claim 3 in which there are provided a driving member of said variable speed gear provided between the feed roller and said driving shaft, a pointed moving jointly with said member, i. e. in relation with the ratio between the production speed and the feeding speed, another variable speed gear provided between the building motion and said driving shaft, a driving member of said last mentioned variable speed gear, the other pointer of the same pair moving jointly with the last mentioned driving member, i. e. in terms of the frequency of the movement direction reversals of the building motion, curves, each corresponding to the workable drafting and winding-on conditions for a particular roving, said curves being drawn on the panel relating to said two pointers, the intersection of the pointers showing on said curves the particular conditions obtained.

6. Spinning frame as claimed in claim 5, in which said second pointer controls the progressive spreading of the spindle and thread guide rails.

7. Spinning frame as claimed in claim 6, in which control of said progressive spreading by said second pointer can be made temporarily inoperative so as to enable adjustment of said control independently of the adjustment of the frequency of the movement direction reversals of the building motion.

8. Spinning frame as claimed in claim 1, in which the motor driving the crown gear of the differential gear is an electric motor and in which there is provided an electronic device for automatically regulating the speed of said electric motor.

9. Spinning frame as claimed in claim 1, in which there is provided an alternating motion cam driving the building motion, and a member rendered operative by the building motion itself and controlling the reversal of the rotation direction of said cam.

10. Spinning frame as claimed in claim 9, in which there are provided a slide included in the building motion, fixed guides between which said slide passes, a roller carried by said slide and cooperating with said cam, a first threaded member mounted within the slide so as to follow the translation movement thereof, a second threaded member cooperating with said first threaded member and mounted so as to be unable to rotate, a spindle rail supported by said second threaded member, a thread guide rail, means actuated by said slide for rotating said first threaded member for producing a progressive separation of the spindle rail and the thread guide rail.

11. Spinning frame as claimed in claim 10, in which said first threaded member is rotated during each of the slide movements along either one of the opposite directions, i. e. either during the outwards travels, or during the inwards travels.

l2. Spinning frame as claimed in claim 10, in which there is provided a device enabling, when the distance between the spindle and thread guide rails is at its working maximum, that is when a bobbin is completed, to rotate said first threaded member so as to increase the distance between the spindle and thread guide rails sufiiciently to allow to release the bobbins.

13. Spinning frame as claimed in claim 12 in which said device enables to rotate said first threaded member along the direction opposite to that of the preceding one, for lowering the distance between the spindle and thread guide rails down to its minimum amount corresponding to the start of a thread Winding.

14. Spinning frame as claimed in claim 12, in which there is provided a device enabling, when the distance between the spindle and thread guide rails is at the working maximum, that is when a bobbin is completed, to rotate said first threaded member so as to increase the distance between the spindle and thread guide rails sufficiently to allow to release the bobbins, said device being arranged so as to be operative only when said unidirectional coupling has been brought to the uncoupling position.

15. Spinning frame as claimed inclaim 14, in which an electric motor constitutes said device, the supply circuit of said motor being closed only when the unidirectional coupling has been brought to the uncoupling position.

16. Spinning frame as claimed in claim 15, in which there are provided a sliding collar in the unidirectional coupling, an electromagnet, a core in said electromagnet for moving said sliding collar, an electric locking device cutting off the supply to the electric motor as long as the electromagnet core has not reached the end of its travel. 7

l7. Spinning frame as claimed in claim 10, in which there are provided coupling means controlling the reversal of the motion direction of the cam, a sliding collar in said coupling means, an arm for effecting movement of said sliding collar, a rod for driving said arm, two stops carried by said rod, 2. part moving jointly with said slide and sliding between said stops with respect to said rod, springs arranged between said part and said stops, locking means preventing alternatively either of the stops from moving, unlocking means alternatively making inoperative said locking means, the movement of said unlocking means being controlled by that of the slide, in such a way that unlocking of one stop occurs when the corresponding spring is set.

18. Spinning frame as claimed in claim 17, having a plate integral with the slide and arranged parallel to said rod, two notches provided in the rod, two others in the plate, the depth of the four notches being substantially the same, a single bolt forming the locking and unlocking means and being held in such a way that a movement thereof parallel with said rod is prevented, said bolt being slidable at right angle to said rod and having a length equal to the distance between those rod and plate faces provided with the notches, increased by the depth of a single notch, the locations of the four notches being selected so that the bolt locks the rod while one of the springs is set and is engaged in one of the notches when the slide comes to one end of its travel so as to enable the release of said spring and the movement of said sliding collar, the bolt being then engaged in the second notch of the rod and releasing the plate, and thus the slide.

19. Spinning frame as claimed in claim 10, in which there are provided a .coupling device controlling the reversal of the motion direction of the cam, a sliding collar in said coupling device, an arm for effecting movement of said sliding collar, two electromagnets, either one of which driving said arm in either direction, supply circuits for said electromagnets, a single two Way (s. p. d. t.) switch being cut in said supply circuits, two elements moving with said slide, either one of said two elements moving said switch in either direction so as to close either of said supply circuits.

20. Spinning frame as claimed in claim 1, in which there are provided a twist barring or twist reducing device between the feed roller and the thread guides, a first rod forming part of said twist barring device, said rod being disposed at right angle to the axes of the spindles and thread guides and parallel to the plane of said axes, a series of supporting rods, fixed bearings in which said supporting rods slide, holes provided at one end of said supporting rods, said first rod being shoved into said holes, levers, a common shaft on which said levers are forced, the second end of said supporting rods resting on the end of said levers, and a working arm for enabling rotation of said shaft for controlling the height of the twist barring.

21. Spinning frame as claimed in claim 10, in which there is provided a running way integral with the slide, said running way being inclined with respect to the movement direction of said slide, a roller slidable along a direction which is at right angle with that of the slide movement and kept in contact with the running way, a pliable strap driven by said roller, a drum around which said strap is trained, means for biasing said drum, a unidirectional coupling through which said drum is driven, and a shaft driving said first threaded member and driven by said drum against said biasing means and through said unidirectional coupling.

22. Spinning frame as claimed in claim 21, wherein means for adjusting the running way slope with respect to the slide movement direction are provided.

23. Spinning frame as claimed in claim 22, in which there are provided supporting means for the running way,

a screw, a stud hole made fast with respect to said supporting means, said running way being adapted to swivel, at one of its ends, with respect to said supporting means, and a nut for said screw, said nut being on the other end of said running way, said screw going through said stud hole and being held lengthwise.

24. Spinning frame as claimed in claim 22, in which there is provided a driving member of the variable speed gear provided between the feed roller and said driving shaft, a pointer moving jointly with said member, i. e. in relation with the ratio between the production speed and the feeding speed, another variable speed gear provided between the building motion and said driving shaft, a driving member of said last mentioned speed gear, the other pointer of the same pair moving jointly with said last mentioned driving member, i. e. in terms of the frequency of the movement direction reversals of the building motion, curves, each corresponding to the workable drafting and winding-on conditions for a particular roving, said curves being drawn on the panel relating to said two pointers, the intersection of the pointers showing on said curves the particular conditions obtained, and control means for the slope of the running way with respect to the slide movement being normally coupled to the second pointer, but being uncouplable at will therefrom.

25. Spinning frame as claimed in claim 1, in which the thread guides are each made up of a hollow revolution body, coaxial with the corresponding spindle and the inside surface of which is in the form of a truncated cone along all of its effective length, and a thread guide hook carlied on the lower part of said body.

26. Spinning frame as claimed in claim 25, in which said thread guide hook is double so as to be usable for any rotation direction of the bread guide.

27. Spinning frame as claimed in claim 25, in which there is provided a bushing included in the guide hook, a hole in the lower part of the thread guide, and adjacent the free edge of said thread guide, said hole being shaped correspondingly relative to said bushing, said bushing being engaged in said hole, and a hold-down device insuring coupling of said thread guide hook and said thread guide.

28. Textile spinning frame or machine for conical layer bobbins comprising rotating spindles, rotating thread guides, a feed roller doubling as a delivery roller, :1 building motion, means for driving positively the spindles, means for driving positively the thread guides, means for driving positively and simultaneously the feed roller and the building motion, means for changing the feed roller speed so that the delivery speed of the latter is slower than the thread winding speed, means for automatically controlling, with respect to one another, the spindle speed and the thread guide speed according to the instantaneous diameter of the coil being wound on, so as to maintain a constant winding speed for the whole length of the building motion travel, said latter means being controlled simultaneously by the building motion and by the means driving both the feed roller and the building motion.

References Cited in the file of this patent UNITED STATES PATENTS 

